CN106285912A - A kind of side volume combustion system of opposed-piston engine - Google Patents
A kind of side volume combustion system of opposed-piston engine Download PDFInfo
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- CN106285912A CN106285912A CN201610607591.8A CN201610607591A CN106285912A CN 106285912 A CN106285912 A CN 106285912A CN 201610607591 A CN201610607591 A CN 201610607591A CN 106285912 A CN106285912 A CN 106285912A
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- piston
- face
- roll face
- exhaust pition
- opposed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
The invention discloses the side volume combustion system of a kind of opposed-piston engine, this system includes fuel injector, inlet piston, exhaust pition, the end face of described inlet piston and exhaust pition is provided with lower concave part radially symmetrically, lower concave part forms an arc notch formed after passing through mutually with column jacket side face on inlet piston with exhaust pition, the bottom surface of arc notch is taper surface, and taper surface is towards inlet piston and the direction of exhaust pition end face；The side of arc notch is the roll face, side of the arc surface composition of continuous indent, is arc transition between roll face, side and taper surface；Fuel injector is arranged between inlet piston and exhaust pition and the apex of corresponding lower concave part taper surface.The present invention improves air utilization ratio by the roll face, side on inlet and outlet piston, accelerates fuel oil and the mixing velocity of air, the burning improving opposed-piston engine with this and discharge performance.
Description
Technical field
The present invention relates to the combustion system of a kind of internal combustion engine, be specifically related to the combustion system of a kind of opposed-piston engine,
Belong to Structure of Internal-Combustion Engine technical field.
Background technology
Opposed-piston diesel can improve combustibility and emission performance effectively.Compared with conventional diesel engine, opposed
Piston diesel engine distinct issues are still that the distribution of fuel oil, spread and mix.Improve the utilization rate of the bags, add fast burn
The mixing velocity of oil and air can improve the dynamic property of diesel engine, economy and emission performance effectively.
Diesel engine applies various method to improve the coupling of fuel oil, air, combustor, thus improve engine combustion
And discharge performance, but these technology still suffer from the problems such as petroleum distribution is uneven, air utilization ratio is the highest to a certain extent.Existing
Opposed-piston diesel in inlet piston and exhaust pition end face be the sphere of indent, its structure is as it is shown on figure 3, by entering
The combustor that the end face of gas piston and exhaust pition surrounds then defines flat ball shape structure, as it is shown in figure 1, combustor is divided into
A district and B district, A district is the central area of combustor, and B is the marginal area of combustor.From figure 2 it can be seen that the body in B region
Long-pending account for combustion chamber volume 0.25～0.5 times.Owing to opposed-piston diesel makes oil bundle axially cut from side injection
The distribution in face is generally 0 °～60 °, and the air utilization ratio thus resulting in B region declines.
Summary of the invention
In view of this, the invention provides the side volume combustion system of a kind of opposed-piston engine, it is possible to pass through inlet and outlet
Air utilization ratio is improved in roll face, side on piston, accelerates fuel oil and the mixing velocity of air, improves opposed pistons with this
The burning of electromotor and discharge performance.
A kind of side volume combustion system of opposed-piston engine, this system includes fuel injector, inlet piston, exhaust pition,
The end face of described inlet piston and exhaust pition is provided with lower concave part radially symmetrically, and lower concave part is at inlet piston and exhaust pition
The arc notch that upper formation one is formed after passing through mutually with external cylindrical surface, the bottom surface of arc notch is taper surface, and taper surface is towards entering
Gas piston and the direction of exhaust pition end face；The side of arc notch is the roll face, side of the arc surface composition of continuous indent, phase
Two adjacent arc surface composition roll face, one side unit, are arc transition between roll face, side and taper surface；Fuel injector is arranged
Between inlet piston and exhaust pition and the apex of corresponding lower concave part taper surface.
Further, jet length R of described fuel injector meets: 0.45D > R > 0.85L, D are piston diameter, and L is fuel oil
The liquid phase penetration distance of spraying；Height h=(0.045～0.083) D, arc surface r1=(0.038～0.114) in roll face, side
D, arc surface cornerite β=20 °～30 °, the number n=4～6 of roll face, side unit in unilateral roll face, side.
Further, quantity and the distribution situation of the oil bundle that roll face, described side sprays according to fuel injector is symmetrical expression or non-
Symmetrical expression.
Further, cone height H2=(0.027～the 0.053) D of described taper surface, conical bottom edge lengths L2 meets: R
> L2 > 0.292D, combustion-chamber depth H1=(0.091～0.129) D, combustor radius L1=R+h, δ are piston clearance.
Further, the spray orifice of described fuel injector is two rows, and the roll face, side of row's correspondence inlet piston, a row is corresponding
The roll face, side of exhaust pition, the orifice number of fuel injector is: n/2, n are the number of roll face, side unit in unilateral roll face, side；
Oil bundle angle: the angle of two oily interfasciculars of lateral cross section is 2 × β；Longitudinal cross-section oil bundle angle is α=70 °～82 °.
Beneficial effect:
The present invention promotes fuel oil to both sides scrolling by roll face, side, is conducive to improving the utilization of the bags, and
Accelerate the flowing of burning room air.Taper surface contributes to reducing without fuel space volume so that air focuses on fuel distribution
More position.Above-mentioned both sides structure is improved and is effectively improved combustion process, improves the economy of electromotor, dynamic property
And discharge performance.
Accompanying drawing explanation
Fig. 1 is existing flat spherical combustion chamber and piston structure schematic diagram thereof；
Fig. 2 is the division schematic diagram of flat spherical combustion chamber central area and marginal area；
Fig. 3 is the three dimensional structure schematic diagram of inlet piston and exhaust pition in flat spherical combustion chamber
The opposite side that Fig. 4 provides for the present invention rolls up combustor and piston schematic diagram thereof；
Fig. 5 is the top view of exhaust pition of the present invention；
Fig. 6 be inlet piston of the present invention or exhaust pition or three dimensional structure schematic diagram；
Fig. 7 is the schematic diagram of opposite side volume chamber structure parameter；
Fig. 8 is the threedimensional model of opposite side volume combustor；
Fig. 9 is flat spherical combustion chamber and opposite side volume combustor indicated horsepower comparison diagram；
Figure 10 is average pressure curve in flat spherical combustion chamber and opposite side volume combustor cylinder；
Figure 11 is mean temperature curve in flat spherical combustion chamber and opposite side volume combustor cylinder；
Figure 12 is flat spherical combustion chamber and opposite side volume combustor instantaneous exothermic heat rate curve；
Figure 13 is flat spherical combustion chamber and opposite side volume combustor cumulative heat release curve；
Figure 14 is flat spherical combustion chamber and opposite side volume combustor Soot mass fraction correlation curve.
Wherein, 1-fuel injector, 2-inlet piston, 3-exhaust pition, roll face, 4-side, 5-taper surface,
Detailed description of the invention
Develop simultaneously embodiment below in conjunction with the accompanying drawings, describes the present invention.
As shown in Figure 4, the invention provides the side volume combustion system of a kind of opposed-piston engine, this system includes spray
Oil device 1, inlet piston 2 and exhaust pition 3, the end face of inlet piston 2 and exhaust pition 3 is provided with lower concave part radially symmetrically,
Lower concave part forms an arc notch formed after passing through mutually with external cylindrical surface, arc notch on inlet piston 2 with exhaust pition 3
Bottom surface be taper surface 5, taper surface is towards inlet piston 2 and the direction of exhaust pition 3 end face；As shown in Figure 5, arc notch
The roll face, side 4 of the arc surface that side is continuous indent composition, the most adjacent two arc surfaces composition roll faces, one side are single
Unit, has six arc surfaces, forms roll face, five sides unit altogether in figure；As shown in Figure 6, side roll face 4 and taper surface 5 it
Between be arc transition；Fuel injector 1 is arranged between inlet piston and exhaust pition and the apex of corresponding lower concave part taper surface, attached
Fig. 8 is the threedimensional model of opposite side volume combustor, the corresponding redundance machined away from inlet piston 2 and exhaust pition 3.
As shown in Figure 7, side roll face 4 requires each oil bundle corresponding roll face, side unit that fuel injector 1 sprays
Central protuberance part, and have vacant roll face, a side unit between two oil bundles to prevent adjacent oil bundle from occurring
Degree overlap is concentrated.
Jet length R of fuel injector meets: 0.45D > R > 0.85L, D are piston diameter, and L is that the liquid phase of fuel spray runs through
Distance；Height h=(0.045～0.083) D, arc surface r1=(0.038～the 0.114) D in roll face, side, arc surface cornerite β=
20 °～30 °, the number n=5 of roll face, side unit in unilateral roll face, side.The oil bundle that roll face, side sprays according to fuel injector
Quantity and distribution situation are symmetrical expression.
Cone height H2=(0.027～the 0.053) D of taper surface, conical bottom edge lengths L2 meets: R > L2 > 0.292D, combustion
Burning room depth H 1=(0.091～0.129) D, combustor radius L1=R+h, δ are piston clearance.
The spray orifice of fuel injector is two rows, the roll face, side of row's correspondence inlet piston, the side of the exhaust pition that a row is corresponding
Roll face；The orifice number of fuel injector is: n/2, owing in unilateral roll face, side, the number of roll face, side unit is 5, so spray
Hole count takes 3；Oil bundle angle: the angle of two oily interfasciculars of lateral cross section is 2 × β；Longitudinal cross-section oil bundle angle be α=70 °～
82°。
Set up the opposite side volume combustor under the conditions of identical compression ratio and the CFD three-dimensional grid mould of flat spherical combustion chamber respectively
Type, carries out simulation calculation contrast, three-dimensional modeling is set up be close to two kinds of combustor under the conditions of equal grid carry out calculating so that
Being compared, other calculating and setting are identical.Thus obtain in the indicated horsepower of two kinds of combustor, cylinder average in average pressure, cylinder
Temperature, instantaneous exothermic heat rate, Cumulative heat release, Soot mass fraction comparison diagram.
Wherein accompanying drawing 9 is opposite side volume combustor and the indicated horsepower comparison diagram of flat spherical combustion chamber.It is computed, from air inlet
Mouth was closed within the calculating time period of Exhaust Open, and the indicated horsepower of opposite side volume combustor and flat spherical combustion chamber is respectively
72.18kW and 71.43kW, the power of opposite side volume combustor is higher than flat spherical combustion chamber by 1.05%.
Accompanying drawing 10 is tried hard to for mean pressure in opposite side volume combustor and flat spherical combustion chamber cylinder, it can be seen that right
In putting side volume combustor vat, average pressure can reach 77.9bar, and flat spherical combustion chamber is 70.2bar.In whole burning
During, in the cylinder of opposite side volume combustor, average pressure is higher than average pressure in flat spherical combustion chamber cylinder.
Accompanying drawing 11 is mean temperature figure in opposite side volume combustor and flat spherical combustion chamber cylinder, it can be seen that 170
In cylinder before DEG C A, mean temperature is more or less the same, and during 170 DEG C of A to 217 DEG C of A, opposite side volume combustor mean temperature is higher than oblate spheroid type
Combustor, but after 217 DEG C of A, its burning mean temperature is less than flat spherical combustion chamber, illustrates that opposite side volume combustor early stage burning is fast.
Accompanying drawing 12 and Figure 13 is respectively instantaneous exothermic heat rate and the accumulated heat release discharge curve of two kinds of combustor, at the beginning of combustion heat release
The burning instantaneous exothermic heat rate of phase flat spherical combustion chamber is basically identical, and starts to squeeze stream combustor heat release from 172 DEG C of A and height comparatively fast occur
Exothermic peak in flat spherical combustion chamber.Squeeze stream combustor subsequently and have higher burning in during this period of time at 169 DEG C of A to 182 DEG C of A
Heat liberation rate, heat release rate so that it is higher than flat spherical combustion chamber on cumulative heat release, from cumulative heat release, opposite side volume combustor is more than
Flat spherical combustion chamber.
Accompanying drawing 14 is opposite side volume combustor and the Soot mass fraction curve of flat spherical combustion chamber, can from figure
Going out, in whole combustion process, the Soot of opposite side volume combustor is lower than the Soot that flat spherical combustion chamber discharges, and opposite side is described
The comparison of volume combustion chambers burn is abundant.
In sum, these are only presently preferred embodiments of the present invention, be not intended to limit protection scope of the present invention.
All within the spirit and principles in the present invention, any modification, equivalent substitution and improvement etc. made, should be included in the present invention's
Within protection domain.
Claims (5)
1. an opposed-piston engine side volume combustion system, it is characterised in that this system include fuel injector, inlet piston,
Exhaust pition, the end face of described inlet piston and exhaust pition is provided with lower concave part radially symmetrically, and lower concave part is at inlet piston
With on exhaust pition formed one pass through mutually with outer circumference surface after formed arc notch, the bottom surface of arc notch is taper surface, bore
Shape is facing to inlet piston and the direction of exhaust pition end face；The side of arc notch is the side of the arc surface composition of continuous indent
Roll face, two adjacent arc surface composition roll face, one side unit, are arc transition between roll face, side and taper surface；Spray
Oil device is arranged between inlet piston and exhaust pition and the apex of corresponding lower concave part taper surface.
2. the side volume combustion system of opposed-piston engine as claimed in claim 1, it is characterised in that the spray of described fuel injector
Penetrate distance R to meet: 0.45D > R > 0.85L, D are piston diameter, and L is the liquid phase penetration distance of fuel spray；The height in roll face, side
Degree h=(0.045～0.083) D, arc surface r1=(0.038～0.114) D, arc surface cornerite β=20 °～30 °, unilateral side volume
The number n=4～6 of side roll face unit in profile.
3. the side volume combustion system of opposed-piston engine as claimed in claim 1 or 2, it is characterised in that described side roll
Quantity and the distribution situation of the oil bundle that face sprays according to fuel injector are symmetrical expression or asymmetric.
4. the side volume combustion system of opposed-piston engine as claimed in claim 3, it is characterised in that the circle of described taper surface
Cone height H2=(0.027～0.053) D, conical bottom edge lengths L2 meets: R > L2 > 0.292D, combustion-chamber depth H1=(0.091
～0.129) D, combustor radius L1=R+h, δ are piston clearance.
5. the side volume combustion system of opposed-piston engine as claimed in claim 4, it is characterised in that the spray of described fuel injector
Hole is two rows, the roll face, side of row's correspondence inlet piston, the roll face, side of the exhaust pition that another row is corresponding；The spray of fuel injector
Hole count is: n/2, n are the number of roll face, side unit in unilateral roll face, side；Oil bundle angle: two oily interfasciculars of lateral cross section
Angle is 2 × β；Longitudinal cross-section oil bundle angle is α=70 °～82 °.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2016102520813 | 2016-04-22 | ||
| CN201610252081 | 2016-04-22 |
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| Publication Number | Publication Date |
|---|---|
| CN106285912A true CN106285912A (en) | 2017-01-04 |
| CN106285912B CN106285912B (en) | 2019-12-31 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610607591.8A Active CN106285912B (en) | 2016-04-22 | 2016-07-28 | Side-winding combustion system of opposed-piston engine |
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| CN (1) | CN106285912B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106837519A (en) * | 2017-03-15 | 2017-06-13 | 中北大学 | A kind of opposed pistons two stroke diesel engine swirl combustion system |
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| CN101839166A (en) * | 2009-11-06 | 2010-09-22 | 北京理工大学 | Lateral-swirl combustion chamber |
| CN102900521A (en) * | 2011-07-26 | 2013-01-30 | 艾克莫特国际公司 | Tumble-flow accelerating combustion chamber |
| CN102947545A (en) * | 2010-04-27 | 2013-02-27 | 阿凯提兹动力公司 | Combustion chamber constructions for opposed-piston engines |
| CN103046996A (en) * | 2011-10-17 | 2013-04-17 | 通用汽车环球科技运作有限责任公司 | Combustion system for an engine having multiple fuel spray induced vortices |
| CN103562515A (en) * | 2011-05-18 | 2014-02-05 | 阿凯提兹动力公司 | Combustion chamber construction for opposed-piston engines |
| US20150122227A1 (en) * | 2013-11-07 | 2015-05-07 | Achates Power, Inc. | Combustion Chamber Construction with Dual Mixing Regions for Opposed-Piston Engines |
| CN105422258A (en) * | 2015-12-14 | 2016-03-23 | 中国北方发动机研究所(天津) | Double T-shaped combustion chamber applicable to opposed injection |
-
2016
- 2016-07-28 CN CN201610607591.8A patent/CN106285912B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101839166A (en) * | 2009-11-06 | 2010-09-22 | 北京理工大学 | Lateral-swirl combustion chamber |
| CN102947545A (en) * | 2010-04-27 | 2013-02-27 | 阿凯提兹动力公司 | Combustion chamber constructions for opposed-piston engines |
| CN103562515A (en) * | 2011-05-18 | 2014-02-05 | 阿凯提兹动力公司 | Combustion chamber construction for opposed-piston engines |
| CN102900521A (en) * | 2011-07-26 | 2013-01-30 | 艾克莫特国际公司 | Tumble-flow accelerating combustion chamber |
| CN103046996A (en) * | 2011-10-17 | 2013-04-17 | 通用汽车环球科技运作有限责任公司 | Combustion system for an engine having multiple fuel spray induced vortices |
| US20150122227A1 (en) * | 2013-11-07 | 2015-05-07 | Achates Power, Inc. | Combustion Chamber Construction with Dual Mixing Regions for Opposed-Piston Engines |
| CN105422258A (en) * | 2015-12-14 | 2016-03-23 | 中国北方发动机研究所(天津) | Double T-shaped combustion chamber applicable to opposed injection |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106837519A (en) * | 2017-03-15 | 2017-06-13 | 中北大学 | A kind of opposed pistons two stroke diesel engine swirl combustion system |
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